Pump



H. E. JEPSEN 3,203,356

Aug. 31, 1965 3 Sheets-Sheet 1 Dec. 27, 1960 1955 H. E. JEPSEN 3,203,356

Filed Dec. 27, 1960 3 Sheets-Sheet 2 31, 1965 H. E. JEPSEN 3,203,356

PUMP

Filed Dec. 27, 1960 3 Sheets-Sheet 3 4770/71 elg.

United States Patent i 3,203,356 PUMP Henry E. lepseu, 10902 S. La SernaDrive, Whittier, Calif. Filed Dec. 27, 1960, Ser. No. 78,351 3 Claims.(Cl. 103-148) The present invention relates to a pump of the rotarytype.

A diificult problem in pump design is to obtain a relatively simple andinexpensive pump structure which will produce a high head or outputpressure. Another consideration of utmost importance is the operatingefiiciency of the pump from the energy standpoint.

One object of the invention, therefore, is to provide a rotary pumpwhich is capable of producing a high head or output pressure.

Another object of the present invention is to provide a rotary pumpwhich will make efficient use of the applied operating energy, evenafter the pump has started to wear.

Another object of the invention is to achieve a speed reduction insidethe pump through the planetary gear principle, thus reducing the totalcost, weight and space requirements for an installation.

A further object of the invention is to provide a rotary pump in whichthe pumping action is produced through the expansion and contraction ofa hollow, flexible, fluidholding body, and by the isolated quantities offiuid carried between these members to the discharge port.

Still another object of the invention is to provide a rotary pumputilizing an eccentric planetary arrangement, in which the planetarymembers are hollow and flexible and operate to successively expand andcontract during their rotation so as to provide the pumping action.

An additional object of the invention is to provide an expansible hollowgear member, which partially com pensates for pump wear.

Still a further, and somewhat unrelated, object of the invention is toprovide a novel rotary fluid seal arrangement.

The above and other objects and advantages of the invention will be morereadily apparent from the following description considered inconjunction with the accompanying drawings, in which:

FIGURE 1 is a perspective view of a presently preferred embodiment of myinvention;

FIGURE 2 is an exterior side elevational view of the pump of FIGURE 1;

FIGURE 3 is a transverse cross-sectional view of the invention taken onthe line 33 of FIGURE 2;

FIGURE 4 is a longitudinal cross-sectional view of the invention takenon the line 4-4 of FIGURE 1;

FIGURE 5 is a schematic diagram illustrating the eccentric arrangementof the rotor housing;

FIGURE 6 is a perspective view of one of the flexible planetary bodies;

FIGURE 7 is an end view of the flexible member of FIGURE 6;

FIGURE 8 is an enlarged fragmentary view of the flexible member takenwithin the circle 8 of FIGURE 7;

and

FIGURE 9 is an enlarged fragmentary cross-sectional view taken withincircle 9 of FIGURE 4, illustrating the rotary seal arrangement.

Referring now to the drawings, the invention generally includes a base Kfrom which a housing L is supported, the exterior configuration of thehousing L being substantially cylindrical. Inlet and outlet ports M andN project from the housing L, as well as a drive shaft P. Inside thehousing the drive shaft P carries a rotor Q.

The configuration of the rotor Q is cylindrical, but the 3,203,356Patented Aug. 31, 1965 interior surface of housing L is onlyapproximately cylindrical, being intentionally provided with aneccentric configuration as will be more particularly described in connection with FIGURE 5. The inlet and outlet pipes M and N communicatewith the interior of housing L through respective openings in and n,which communicate directly with that portion of the interior of thehousing that surrounds the rotor Q. Three flexible planetary members Rare disposed within the housing L, in circumferentially spaced positionsaround the rotor Q. Each planetary member R has a normally cylindricalconfiguration, but is compressed radially of rotor Q so as to assume anapproximately elliptical shape.

The end structures of the housing L which, include both means forrotatably supporting the shaft P and also means for sealing againstleakage along the shaft, are respectively designated as S and T.

Although direction of rotation is optional, FIGURE 3 shows the rotor Qrotating counterclockwise, indicated by an arrow 20. Each of theplanetary members R has a hollow interior, and its running height isincreased at it passes the inlet opening m, drawing fluid through theinlet opening in from the inlet pipe M. The planetary member thenrevolves around the lower side of rotor Q, and as it approaches theoutlet opening n its running height decreases, or is flattened, causingit to discharge fluid through the outlet opening 11 and hence to theoutlet pipe N. The configuration of the interior surface of housing L issuch that after each planetary member passes upward beyond the outletopening 12, its running height remains constant while it revolves overthe rotor Q and descends on the other side and starts to overlap theinlet opening m. Also, after passing below the inlet opening in itsrunning height remains constant while it revolves across the undersideof rotor Q and starts to overlap the outlet opening 21. In other words,each planetary mem ber R experiences a change in its running height onlyduring the time when it is at least partially overlapping one of theopenings m and 11.

Reference is now made to FIGURE 5 in order to more completely describethe interior configuration of housing L and the positioning of rotor Qrelative thereto. In FIGURE 5 the exterior circumference of housing L isidentified as 21, and its axis is identified as 22. The center line ofshaft P and rotor Q is identified as 23. The inner wall of housing Lincludes an upper fixed radius portion 24, a lower fixed radius portion25, a lefthand tapered portion 26, and a right-hand tapered portion 27.Upper wall portion 24 has a fixed radius A about the center point 23.Lower wall portion 25 has a fixed radius B about the centerpoint 23, theradius B being larger than radius A.

Upper wall portion 24 extends from a point located a vertical distance Dabove the center point 23, around the top of housing L to another pointwhich is the same distance D above center point 23. Lower wall portion25 extends from a point a distance D below the center 23, at the left ofhousing L, to a point the same distance below center 23 at the right ofhousing L. Tapered portions 26 and 27 join the corresponding ends of thefixed radius portions 24 and 25 together. Each of the tapered portions26 and 27 has a radius value C, which is greater than radius A but lessthan radius B. The center point 28 for radius C of the tapers 26 and 27is located somewhat below the center point 23 of the rotor Q.

In the illustrated embodiment of the invention the various dimensionsare as follows: radius A, 1.885 inches; radius B, 2.035 inches; radiusC, 1.969 inches; distance D, 0.750 inch. The vertical ofl'set betweencenter points 23 and 28 is about 0.193 inch.

In the illustrated embodiment of the invention the rotor Q is providedwith circumferentially spaced teeth 30, the planetary members R withteeth 31, and the inner circumferential surface of housing L with teeth32. The housing surface portions 24-27 as illustrated in :FIGURE 5establish the locations of the faces of teeth 32. In the illustratedembodiment of the invention the basic circular pitch of'the housingteeth'32 is about 0.285 inch. It is'interestingto note that for designreasons the circular pitch of the teeth in the upper or small radiusportion24 of the housing inner surface is about one-half percent greaterthan the basic value. Also, that the circular pitch of the flexiblemember matches perfectly with both the rotor and housing in the stressedposition; but not in the unstressed state.

It will be seen that the end radii of each of the flexible planetarymembers R change'while moving past either of the tapered radiusportions26 or27 of the housing L.

' As seen in'FIGURE '3 the planetary members R are compressed to anapproximately elliptical configuration, so that while the pump isoperating the radius value of each planetary member R measure'd withreference to the center axis 23'of rotorQ is somewhere between onethirdand one-half the radius value that the planetary member R would have inan unstressed cylindrical form 'as illustrated in FIGURE 6. Not only dothe end radii ofthe planetary members experience a change as they passthe openings in and n, locatedrespectively adjacent to' the taperedradius'portions '26 and '27 of housing L, but they also experience aslight change in forward speed. That is, in traveling above the rotor Q,under the small radius portion 24 of housing'L, the planetary memberismoving around a smaller circular path, and therefore travels at higherlineal velocity. In traveling underneath rotor Q past'the' large radiusportion25 of the housing the planetary members travel at a slightlyslower velocity. In travelingpast the tapered radius portions adja-'cent the inlet and outlet openings each planetary mem- "berthereforeexperiences some change in "forward or rotational velocity as well'as inits mean radius and hence il'll'ltS fluid carrying capacity.

The three'planetary members R a're'identical, and reference is now madeto FIGURES 6 and 8, inclusive, for the'purpose'of describing thestructure thereof. A thin rectangular spring steel sheet member '40 isrolled into a multi-layer cylinder. Adjacent the inner end 41 of thesheet'member 40 a longitudinally spaced series of welds 43 are made,which not only bond the inner end 41 to the immediately adjacent layerof member'40, but also bond all of the layers of member40 together.Welds 43 are preferably achieved by electric spot welding technique.Adjacent the outer end 42 of member '40 a similar series of welds 44 areformed. Again, welds'44 pass through all of the layers of member 40, andare preferably formed by electric spot welding.

A plurality of elongate rigid members provide the teeth for flexibleplanetary'rnembers' R. Each member 50 is'formed'ofmetal and has a lengthapproximately equal to the width of steel sheet member 40 (and henceequal to the length of the cylinder formed'by sheet member 40). Eachmember '50 has a transverse cross-sectional configuration which isapproximately trapezoidal, including aflat outer face 51, and slopedside faces 52 and 53. Undersurface 54 is' welded at 55 to the outersurface of the inulti-layer cylinder formed by sheet member 40.

While in connection'with the present invention it is necessary for theteeth members 50'to be on the outer surface of the multi-layer cylinderformed by sheet member 40*, nevertheless in other applications it wouldbe possible to'utilize' the same flexible g'ear construction but withthe teeth members 50 mounted on the inner cir cumferential surface ofthe cylinder.

It is preferredto 'coat the entire flexible member with Teflon. Thisresults in a better operation of the system.

Reference is now made to FIGURE 9 in order to describe the structure andoperation of the rotary seal arangement T. A cylindrical insert ofsleeve 66 is carried in the associated end of housing L, and shaft Protates within a cylindrical bearing surface formed by the hearingmember 60. The interior of housing L lies to the left of bearing member60, as shown in FIGURE 9, and hence during normal operation of the pumpa supply of pressurized fluid exists on the left'hand side of thebearing member 60. On its right hand side bearing member 69 has a flatouter surface 61 which extends circumferentially about the shaft P andis aligned perpendicular thereto. A thrust washer 62 is loosely fittedon shaft P and circumferentially engages the flat outer surface 61 ofthe bearing member 60 in rotatable and fluid-sealing relationshiptherewith. An elastomeric O-ring 63 encircles shaft P in tightcircumferential engagement therewith, and also in circumferentialengagement with the other side of washer 62, which is not in contactwith surface 61 of the bearing member 60.

A retaining cup 64 is carried by shaft P on the other side of O-ring 63,onto theright as seen in FIGURE 9. Retaining cup 64 has a base portion65 which extends radially outwardly from shaft P, perpendicular to thelongitudinal axis thereof, with the inner circumferential surface ofbase portion 65 tightly engaging the circumferential surface of shaft P.Retaining cup 64 also includes an outer flange portion'66 which,together with the base portion 65, forms a substantially L-shapedcrosssection for the'retaining cup64, taken radiallywith respect to theshaft P. Flange portion '66is aligned substantially parallel to thelongitudinal axis of shaft P, and encloses the outer circumferentialextremity of O- ring 63. The extreme circumferential edge 67 of flangeportion 66' extends to the left of the center of O-ring 63, as seen inFIGURE'9, and is disposed adjacent to but not in engagement with thethrust washer 62. A circumferential groove 68 on the shaft P carries aretaining ring 69, which engages the retaining cup 64 on the outer sidethereof, or 'the right-hand side as seen in FIGURE 9.

Since sealing arrangement S at the other end of housing L is similar tosealing arrangement T, the cooperative functioning of the twosealingarrangements is such that the shaft P maintains a substantially fixedlongitudinal position relative to housing L, and therefore, relative tohearing member 60 as well. It will be seen in FIGURE 9 that there is adefinite end loading of the seal, that is, the sandwich consisting ofO-ring 63, thrust washer 62, and retaining cup 64 iscompressedlongitudinally between the bearing surface 61 of bearingmember 60 and the retaining ring 69.

The operation of the rotary seal is as follows. Pressurized fluidflowing from the left-hand side of bearing member 60 passes betweenbearing member 60 and shaft 'P, and then flows beneath the innercircumferential edge of thrust washer 62, which has a loose fit upon theshaft P. The pressurized fluid continues to flow longitudinally of shaftP and exerts pressure on the nearest circumferential surface portion 70of the O-ring 63. O-ring 63 is therefore caused to deform in a directiontoward the juncture of base portion 65 and flange portion 66 of theretaining cup 64, so that the circumferential surface portion71 of theO-ring presses more tightly in a radially inward direction upon thecircumferential surface of shaft P, and the circumferential surfaceportion '72 of the O-ring in engagement with thrust washer 62 applies agreater force upon' the thrust washer in a direction parallel to thelongitudinal axis of the shaft P. This also causes a greater pressure tobe exerted by the thrust washer 62 upon the-bearing surface 61, thusminimizing the possibility of fluid escaping therebetween. The spacingof extremity 67 of the retaining cup from thrust washer 62 is necessaryin order to permit the O-ring 63 to deform, but at the same time thespacing must be rather small in order to preclude the possibility thatthe O-ring might flow out between the thrust washer and the retainingcup.

The invention has been described in considerable detail in order tocomply with the patent laws by providing a full public disclosure ofatleast one of its forms. However, such detailed description is notintended in any way to limit the broad features of principles of theinvention, or the scope of patent monopoly to be granted.

1 claim:

1. A pump comprising a housing have a somewhat cylindrical interiorchamber; a shaft journalled in both ends of said housing in axialalignment therewith and extending through said interior chamber; acylindrical rotor carried concentrically on said shaft and adapted to bedriven thereby, said rotor having longitudinally extending teethuniformly spaced about its entire circumference; the length of saidinterior chamber being only slightly greater than the length of saidrotor, the circumferential Wall of said chamber having onecircumferential portion which is concentric to said shaft and spaced bya first radius distance from the axis of said rotor, a second andoppositely disposed circumferential portion which is also concentric tosaid shaft but at a second and larger radius distance from the axis ofsaid rotor, and first and second tapered-radius portions which areoppositely disposed to each other and which interconnect saidfixed-radius portions; at least two flexible members disposed incircumferentially spaced positions within said chamber, each of saidflexible members being normally of a substantially cylindricalconfiguration and of substantially the same length as said rotor, butbeing depressed between the periphery of said rotor and said chamberwall into an approximately elliptical form, each of said flexiblemembers having teeth on its exterior surface which engage said rotorteeth; the circumferential wall of said chamber having teeth formedthereon which are engaged by the teeth of said flexible members; a firstopening in an end of said housing communicating with said firsttaperedradius portion of said chamber; and a second opening in an end ofsaid housing communicating with said second tapered-radius portion ofsaid chamber.

2. A pump comprising:

(a) a housing and a rotor disposed eccentrically therein, said housingand rotor having confronting walls defining therebetween an annularchamber;

(b) an inlet and an outlet for said chamber;

(c) each of said confronting walls having alternate ribs and grooves toform a ring of interlocking elements;

(d) and a plurality of flexible bands having, externally,

alternate ribs and grooves forming a ring of interlocking means;

(e) each of said flexible bands being interposed between saidconfronting walls to dispose a group of said interlocking means inintermeshing engagement with a group of the intermeshing elements ofsaid rotor wall and said housing wall whereby said flexible bands areinterlocked against sliding movement with respect to said housing walland said rotor wall;

(f) said flexible bands being adapted, on rotation of said rotor, toroll between said confronting walls and cause succeeding groups of saidelements and means to interlock, whereby said flexible bands form fluidpressure resisting partitions movable between said inlet and outlet.

3. A pump, comprising:

(a) a housing defining an approximately cylindrical chamber;

(b) a ring of teeth formed on the peripheral wall of said chamber;

(0) a rotor disposed eccentrically within said chamber and defining withsaid housing an annular space of Varying radial dimension;

(d) a ring of teeth on the peripheral wall of said rotor and confrontingthe teeth in the peripheral wall of said chamber;

(e) a plurality of flexible annular containers each having a normaldiameter greater than the radial dimension of said annular space;

(f) a ring of teeth on the peripheral wall of each container externallythereof;

(g) said containers being distortable to fit in said annular space withgroups of its teeth intermeshing with groups of said rotor teeth andhousing teeth thereby to provide positive drive connections with saidcontainers on rotation of said rotor and effect circular movement ofsaid containers in said annular space;

(h) said housing having an inlet opening, and an outlet openingcornmunicating axially with said annular space, the radial dimension ofsaid annular space being of increasing value in the direction ofrotation of said rotor in the vicinity of said inlet opening and ofdecreasing value in the vicinity of said outlet opening, whereby saidcontainers, on passing said inlet opening draws fluid from said inlet,and on passing said outlet opening expells fluid therefrom.

References Cited by the Examiner UNITED STATES PATENTS 1,943,227 1/34Parker 308-363 2,157,776 5/39 Steinkamp 74-449 2,215,686 9/40 Buchet30836.3 2,745,355 5/56 Mosbacher 103117 2,918,018 12/59 Miller 1031482,952,163 9/60 Kapeller 74-449 2,962,974 12/60 Porkert 103148 2,988,0036/61 Schmied 103-148 X LAURENCE V. EFNER, Primary Examiner.

WARREN E. COLEMAN, JOSEPH H. BRANSON,

Examiners.

1. A PUMP COMPRISING A HOUSING HAVE A SOMEWHAT CYLINDRICAL INTERIORCHAMBER; A SHAFT JOURNALLED IN BOTH ENDS OF SAID HOUSING IN AXIALALIGNMENT THEREWITH AND EXTENDING THROUGH SAID INTERIOR CHAMBER; ACYLINDRICAL ROTOR CARRIED CONCENTRICALLY ON SAID SHAFT AND ADAPTED TOBEE DRIIVEN THEREBY, SAID ROTOR HAVIING FLONGITUDINALLY EXTENDING TEETHUNIFORMLY SPACED ABOUT ITS ENTIRE CIRCUMFERENCE; THE LENGTH OF SAIDINTERIOR CHAMBE BEING ONLY SLIGHTLY GREATER THAAN THE LENGTH OF SAIDROTOR, THE CIRCUMFERENTIAL WALL OF SAID CHAMBER HAVING ONECIRCUMFERENTIAL PORTION WHICH IS CONCENTRIC TO SAID SHAFT AND SPACCED BYA FIRST RADIUS DISTANCE FROM THE AXIS OF SAID ROTOR, A SECOND ANDOPPOSIITELY DISPOSED CIRCUMFERENTIAL PORRTION WHICH IS ALSO CONCENTRICTO SAID SHAFT BBUT AT A SECOND AND LARGER RADIUS DISTANCE FROM THE AXISOF SAID ROTOR, AND FIRST AND SECONND TAPERED-RADIUS PORTIONS WHICH AREOPPOSITELY DISPOSED TO EACH OTHER AND WHICH INTERCONNECT SAIDFIXED-RADIUS PORTIONS; AT LEAST TWO FLEXIBLE MEMBERS DISPOSED INCIRCUMFERENTIALLY SPACED POSITIONS WITHIN SAID CHAMBBER, EACH OF SAIDFLEXIBLE MEMBERS BEING NORMALLY OF A SUBSTANTTIALLY CYLINDRICALCONFIGURATION AND OF SUBSTANTIALLY TTHE SAME LENGTH AS SAID ROTOR, BUTBEING DEPRESSED BETWEEN THE PERIPHERY OF SAID ROTOR AND SAID CHAMBERWALL INTO AN APPROXIMATELY ELLIPTICAL FORM, EACH OF SAID FLELXIBLEMEMBERS HAVING TEETH ON ITS EXTERIOR SURFACE WHICHENGAGE SAID ROTORTEETH; THE CIRCUMFERENTIAL WALL OFF SAID CHAMBER HAVING TEETH FORMEDTHEREON WHICH ARE ENGAGED BY THE TEETH OF SAID FLEXIBLE MEMBERS; A FIRSTOPENING IN AN END OF SAID HOUSING COMMUNICATING WITH SAID FIRSTTAPEREDRADIUS PORTION OF SAID CHAMBER; AND A SECOND OPENING INN TAPEREDRADIUS PORTIONN OF SAID CHAMBER.